EP2982235B1 - Ramasseuse-presse - Google Patents

Ramasseuse-presse Download PDF

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Publication number
EP2982235B1
EP2982235B1 EP15177355.3A EP15177355A EP2982235B1 EP 2982235 B1 EP2982235 B1 EP 2982235B1 EP 15177355 A EP15177355 A EP 15177355A EP 2982235 B1 EP2982235 B1 EP 2982235B1
Authority
EP
European Patent Office
Prior art keywords
assembly
tensioning
spring
frame
attachment point
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP15177355.3A
Other languages
German (de)
English (en)
Other versions
EP2982235A1 (fr
Inventor
Jennifer R Horner
Henry D Anstey
Jacob D Kappelman
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Deere and Co
Original Assignee
Deere and Co
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Deere and Co filed Critical Deere and Co
Publication of EP2982235A1 publication Critical patent/EP2982235A1/fr
Application granted granted Critical
Publication of EP2982235B1 publication Critical patent/EP2982235B1/fr
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/38—Slack adjusters
    • F16D65/40—Slack adjusters mechanical
    • F16D65/52—Slack adjusters mechanical self-acting in one direction for adjusting excessive play
    • F16D65/58—Slack adjusters mechanical self-acting in one direction for adjusting excessive play with eccentric or helical body
    • A—HUMAN NECESSITIES
    • A01—AGRICULTURE; FORESTRY; ANIMAL HUSBANDRY; HUNTING; TRAPPING; FISHING
    • A01F—PROCESSING OF HARVESTED PRODUCE; HAY OR STRAW PRESSES; DEVICES FOR STORING AGRICULTURAL OR HORTICULTURAL PRODUCE
    • A01F15/00—Baling presses for straw, hay or the like
    • A01F15/07—Rotobalers, i.e. machines for forming cylindrical bales by winding and pressing
    • A01F15/071—Wrapping devices
    • A01F15/0715—Wrapping the bale in the press chamber before opening said chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D49/00—Brakes with a braking member co-operating with the periphery of a drum, wheel-rim, or the like
    • F16D49/08—Brakes with a braking member co-operating with the periphery of a drum, wheel-rim, or the like shaped as an encircling band extending over approximately 360 degrees
    • F16D49/10—Brakes with a braking member co-operating with the periphery of a drum, wheel-rim, or the like shaped as an encircling band extending over approximately 360 degrees mechanically actuated
    • A—HUMAN NECESSITIES
    • A01—AGRICULTURE; FORESTRY; ANIMAL HUSBANDRY; HUNTING; TRAPPING; FISHING
    • A01F—PROCESSING OF HARVESTED PRODUCE; HAY OR STRAW PRESSES; DEVICES FOR STORING AGRICULTURAL OR HORTICULTURAL PRODUCE
    • A01F15/00—Baling presses for straw, hay or the like
    • A01F15/07—Rotobalers, i.e. machines for forming cylindrical bales by winding and pressing
    • A01F15/071—Wrapping devices
    • A01F15/0715—Wrapping the bale in the press chamber before opening said chamber
    • A01F2015/072—Braking means for the film roll in balers which wrap the bale before opening the pressing chamber in order to stretch the film while wrapping

Definitions

  • This disclosure relates to braking and indexing various rotating members, including driven rolls for wrapping baled material within round balers.
  • rotating machinery may be utilized.
  • rotating components may be utilized in round (or other) balers for gathering cut material from a field, forming cylindrical (or other) bales of the material within a baling chamber, and wrapping the formed bales with various types of wrap material.
  • various rollers or other devices may rotate in order to form the material into the bales within the baling chamber.
  • additional rollers or other devices may then rotate to wrap the finished bales with various materials before the bales are ejected from the baling chamber.
  • EP 0 807 380 A1 discloses a baler for forming crop material into cylindrical bales.
  • the baler comprises a baling chamber and means for picking up crop material from a field and conveying said material towards said baling chamber.
  • Wrapping means are installed adjacent said baling chamber for applying wrapping material to the periphery of a completed cylindrical package.
  • Said wrapping means comprise supply means having a supply roll with wrapping material, a dispensing mechanism for receiving the wrapping material from said supply roll and dispensing it to the periphery of said completed cylindrical package.
  • Severing means are provided for severing said wrapping material after an amount thereof has been dispensed about the periphery of said cylindrical package.
  • a drag control means is provided for maintaining the wrapping material stretched while it is being unwound from said supply roll.
  • Said drag control means comprises a friction disc and a brake shoe engaging said friction disc. The force by which said brake shoe is loaded against said friction disc can be varied in accordance with the actual amount of wrapping material remaining on said supply roll.
  • An assembly for braking or indexing rotating members, including one or more rollers included in a baler.
  • a wheel (or pulley) is attached to a rotating component and is surrounded, at least in part, by a traction device such as a brake belt.
  • a tensioning assembly with a lost motion linkage is attached to one end of the traction device and to a frame of a work machine.
  • a counterforce assembly is attached to another end of the traction device and to the frame. Rotating a portion of the tensioning assembly in a braking direction moves the lost motion linkage toward a stop for the lost motion linkage. The stop prevents further movement of the lost motion linkage with respect to the frame, such that the tensioning assembly applies a tensioning force to the traction device.
  • the tensioning force is resisted by the counterforce assembly to impose a braking force on the wheel and thereby brake the rotating component.
  • Rotating the portion of the tensioning assembly in the release direction moves the lost motion linkage away from the stop, thereby reducing the braking force on the wheel.
  • the counterforce assembly may include a mounted member or feed lever attached to the frame.
  • a spring may extend between the mounted member or feed lever and the brake attachment point of the counterforce assembly. When a portion of the tensioning assembly is rotated in the braking direction the spring may provide a resistive force to the traction device to resist the tensioning force from the tensioning assembly.
  • the spring may be pre-compressed when installed on the counterforce assembly, such that the resistive force provided by the spring to the traction device remains relatively constant over a lifespan of the traction device.
  • a feed lever included in the counterforce assembly may be rotated in an indexing direction to apply a tensioning force to the traction device, which may be resisted by a spring of the tensioning assembly to impose an indexing force on the wheel. Rotating the feed lever in a reset direction may release this tensioning force to remove the indexing force from the wheel.
  • a catch may be attached to the frame. A spring in the counterforce assembly may urge the feed lever against the catch when the counterforce assembly is in a braking orientation. Accordingly, the catch may prevent rotation of the feed lever in the reset direction, to allow the counterforce assembly to resist tensioning force applied to the traction device by the tensioning assembly.
  • a power source may automatically provide drive force to the wheel depending on the rotation of the tensioning assembly.
  • a controller may determine a state of an operation including the rotating component and may automatically cause an actuation device to rotate the portion of the tensioning assembly depending on the determined state.
  • indexing and braking assembly or assemblies
  • Various examples herein may refer to assemblies in the context of a round baler for cut plant material and to the braking and indexing of a guide roll of such a baler. It will be understood, however, that the disclosed assemblies may be utilized in a variety of settings, with respect to a variety of machinery, and for a variety of rotating components.
  • cut crop (or other) material may be gathered from windrows along a field and may be passed into a baling chamber.
  • a system of belts may rotate and compress the gathered material within the baling chamber in order to form the material into cylindrical bales of various size and density, depending on the configuration of the baler.
  • wrapping material e.g., net wrap
  • various rollers may guide net wrap from a material (i.e., source) roller onto the exterior of a rotating cylindrical bale in order to wrap the entire circumference of the cylinder with the net wrap.
  • a cutting assembly may then sever the net wrap so that the wrapped bale may be ejected from the baling chamber and the process begun anew.
  • a guide roller e.g., a rubber guide roller
  • a system for braking the guide roller at the end of a wrapping operation.
  • these systems may be combined into a single braking and indexing system, which may interoperate with various other components and systems of the relevant baler (or other machinery).
  • a baler may include a guide roller for wrapping material (or another rotating component) that is driven by a power source such as an electric motor, a connection to a power take-off (“PTO") shaft, and so on.
  • a guide roller may be, for example, a rubber (or rubber-coated) roller that guides wrapping material (e.g., net wrap) toward the baling chamber for a wrapping operation as driven by an electrical motor or a mechanical link to a PTO connection (e.g., a geared connection with an intervening clutch assembly).
  • a guide roller may engage with a material roll (e.g., a roll of net wrap) in order to rotate the material roll.
  • a spring-loaded guide roller may press against the wrap material on a material roll and, via the friction provided by this contact, cause the material roll to counter-rotate with the guide roller.
  • the driven guide roller may cause wrapping material to be unwound from the material roll and fed into a wrapping system.
  • one end of a guide roller may include a wheel, such as a pulley or sheave.
  • a wheel may include a connection for driving the guide roller.
  • the wheel may include a pulley configured to engage a drive belt that extends between the pulley and a separate, driven pulley.
  • a brake band or other traction device may partially surround such a wheel and may be attached at one end to a tensioning assembly and at another end to a counterforce assembly.
  • rotation of the tensioning assembly (or a portion thereof) around an attachment point on the baler frame may cause an increase in tension on the brake band (or other traction device), which may be resisted by the counterforce assembly.
  • rotation of the tensioning assembly in a braking direction may cause a spring-loaded, lost-motion linkage in the tensioning assembly to be urged into a stop that limits further motion of the linkage.
  • the tensioning assembly may impose a tensioning force on the traction device. This tensioning force may be resisted by the counterforce assembly (which may also, in certain embodiments, be spring-loaded), such that a braking force is applied by the traction device to the wheel.
  • the traction device may be caused to stop rotation of the wheel and, accordingly, of the guide roller.
  • This may be useful, for example, once a wrapping operation for a particular bale has finished.
  • braking the guide roller may substantially simultaneously stop rotation of the material roll and cease the feeding of additional wrap material into the system.
  • such braking may also correspond to a severing of the wrap material.
  • the tensioning assembly may be linked to a counterknife such that rotation of the tensioning assembly to brake the guide roller corresponds to a severing of the wrap material with the counterknife.
  • Rotation of the counterforce assembly may also cause an increase in tension on the traction device, which may be resisted by the tensioning assembly.
  • a counterforce assembly (which may be spring-loaded) may be rotated in an indexing direction in order to apply a tensioning force to the traction device.
  • This tensioning force may be resisted by the tensioning assembly (e.g., by a spring attached to a lost motion linkage of the tensioning assembly), such that an indexing force is applied to the wheel and to the guide roller.
  • this indexing force may be released and the collective system may be ready for additional indexing operations.
  • the guide roll may be successively advanced by finite rotational amounts. This may be useful, for example, in order to feed wrap material past the guide roller and into the wrapping system when a new material roll has been added to the baler.
  • both types of functionality described above may be available provided by a system including both a tensioning and a counterforce (or indexing) assembly.
  • only one type of functionality may be provided.
  • a counterforce assembly may facilitate a braking operation by resisting a tensioning force applied to a traction device by a tensioning assembly.
  • such a counterforce assembly may not necessarily facilitate indexing of the guide roller, because the counterforce assembly - or appropriate components thereof - may not be appropriately movable.
  • a tensioning assembly may facilitate an indexing operation by resisting a tensioning force applied to a brake (or indexing) device.
  • a spring included in the tensioning assembly may resist tensioning force applied by a counterforce (or other) assembly to index a rotating component.
  • a tensioning assembly may not necessarily facilitate braking of the guide roller, because the tensioning assembly - or appropriate components thereof - may not be appropriately movable.
  • a tensioning assembly may include a pivoting member rotatably attached to a frame of a baler, and a spring-loaded linkage (e.g., a spring-loaded, lost-motion linkage) attached to the pivoting member.
  • the linkage may be engaged with one end of a traction device (e.g., a brake band) surrounding a pulley member that is attached to (and rotates with) a guide roller.
  • a counterforce assembly may include a mounted member attached to the baler frame, with, in certain embodiments, a spring extending between the mounted member and another end of the traction device.
  • rotating the pivoting member of the tensioning assembly in one direction may tension the spring in the spring-loaded linkage in order to impose a tensioning force on the traction device.
  • This tensioning force may be resisted by the mounted member of the counterforce assembly (e.g., as the lost motion linkage is urged into a stop to prevent further motion of the linkage), such that a braking force is applied to the guide roller via the pulley member.
  • This braking force may then be reduced (and released) by rotating the pivoting member in the opposite direction, which may release the lost motion linkage from the stop and thereby reduce the tensioning force on the traction device.
  • the rotation of the pivoting member may occur automatically based on detection or occurrence of certain events or conditions.
  • a controller may monitor a wrapping operation for the baler and determine when a bale has been appropriately wrapped. Upon such a determination, the controller may automatically cause an actuator to rotate the pivoting member in order to brake the guide roller. In this way, the guide roller may be prevented from continuing to direct wrap material toward the baling chamber when the material is not needed (e.g., when a bale within the chamber has already been appropriately wrapped).
  • the pivoting member may form part of an assembly with additional functionality, which may also be controlled by an actuator as noted above.
  • the pivoting member may include a counterknife arm supporting a counterknife.
  • the actuator may rotate the counterknife arm in order to both brake the guide roller and cut the wrap material with the counterknife. In this way, not only may the guide roller be stopped from feeding additional wrap material toward the baling chamber, but the wrap material may be appropriately cut in order to allow the now-wrapped bale in the baling chamber to be ejected from the baler.
  • the counterforce assembly may include a mounted member configured as a pivoting feed lever.
  • a catch on the baler frame may hold the feed lever in place to allow the counterforce assembly (e.g., via an included spring) to resist the tensioning force provided by the tensioning assembly to the traction device and thereby to assist in braking the guide roller.
  • the feed lever may be removed from the catch in order to allow rotation of the feed lever in the indexing direction. As noted above, this may apply an indexing force to the traction device, which may be resisted by the tensioning assembly (or counterforce assembly) in order to index the pulley member (and the guide roller).
  • this indexing rotation may then be alternated with rotation of the feed lever in a reset direction, which may remove the indexing force from the traction device and move the feed lever back to an appropriate location from which to begin another indexing rotation.
  • the feed lever may be returned to the catch in order to allow for subsequent braking of the guide roller.
  • a belt-tensioning device e.g., an idler pulley
  • rotating the tensioning assembly to release the braking force from the pulley member may cause the belt-tensioning device to engage a drive belt for the pulley member and thereby allow rotational force to be transmitted to the pulley member (e.g., from a motor or mechanical drive also associated with the drive belt).
  • the tensioning assembly when the tensioning assembly is rotated to apply the braking force, this may disengage the belt-tensioning device from the drive belt and thereby remove the rotational drive force from the pulley member. This may assist in more effective and efficient braking of the pulley member (and the guide roller).
  • a controller e.g., a computational system, a mechanical controller, an electro-mechanical or electro-hydraulic controller, and so on
  • a power source may be configured to cause a power source to provide power to the pulley member when the tensioning assembly is not engaged in braking the pulley member, and to not provide power to the pulley member when the tensioning assembly is engaged in braking the pulley member.
  • the controller may cause an electric motor to turn off or may cause a transmission element (e.g., a clutch) to disengage, thereby depriving the pulley member of motive power.
  • the controller may cause the motor to turn on or may cause the transmission element to re-engage, thereby returning motive power to the pulley member.
  • baler 10 may include tongue 12 so that baler 10 may be towed during operation by a separate vehicle (e.g., an agricultural work vehicle such as a tractor (not shown)). Baler 10, in certain embodiments, may receive power from such a vehicle via PTO connection 14, which may be connected in various known ways to a PTO shaft of the vehicle. As baler 10 moves (e.g., is towed) across a field, cut crop material may be gathered by intake assembly 16 and guided into baling chamber 18 within frame 20.
  • a separate vehicle e.g., an agricultural work vehicle such as a tractor (not shown)
  • PTO connection 14 may be connected in various known ways to a PTO shaft of the vehicle.
  • baler may include a chassis of baler 10, various support and safety structures, various interior or exterior panels, and so on.
  • various belts (not shown) or other devices may rotate and compress the gathered material into a generally cylindrical bale (not shown). Once the bale has reached an appropriate size, the bale may be wrapped (e.g., using various equipment protected by rear cover 22) and then ejected from baler 10.
  • Compartment 24 may include various components of a wrapping system, such as material roll 36, and guide roller 32.
  • Material roll 36 for example, may be a roll of wrapping material, such as net wrap material.
  • Material roll 36 may be rotated by guide roller 32, which may in turn be driven by a power source such as an electric motor (not shown in FIG. 2 ) or a mechanical or other connection (not shown in FIG. 2 ) to PTO connection 14.
  • braking and indexing assembly 26 which may include counterforce assembly 28 and tensioning assembly 30, may be mounted to frame 20 to the side of compartment 24, in order to allow for selective braking or indexing of guide roller 32. (As noted above, a similar assembly may be utilized with regard to various other rotating components for baler 10 or for other platforms.)
  • pulley member 40 (or a differently configured wheel) may be attached to guide roller 32 such that pulley member 40 co-rotates with guide roller 32.
  • Pulley member 40 may be driven via drive belt 42, which may partially surround both of pulley member 40 and drive pulley 44.
  • Drive pulley 44 may be driven by power source 46, which may include an electrical motor, a gearbox and clutch or other link to PTO connection 14, and so on.
  • power source 46 e.g., an electric motor or mechanical transmission
  • Counterforce assembly 28 which may assist in braking or indexing pulley member 40 (and guide roller 32), may be attached to brake belt 54 (or another traction device) at brake attachment point 56.
  • Counterforce assembly 28 may also include a mounted member attached to frame 20 at frame attachment point 58.
  • a mounted member may be non-movably attached to frame 20 and, as such, provide a fixed anchor for various operations.
  • such a mounted member may be configured as feed lever 52, which may be rotatably mounted to frame 20 at attachment point 58 (e.g., via a bolt and cotter-pin connection).
  • attachment point 58 is a rotatable attachment point
  • an additional attachment may be provided between frame 20 and feed lever 52, such that feed lever 52 may be prevented from rotating as appropriate (and so that feed lever 52 may thereby sometimes provide a relatively fixed anchor for various operations).
  • catch 66 (see also FIG. 4B ) may be provided to prevent upward movement of feed lever 52 (from the perspective of FIG. 3 ) when feed lever 52 is engaged with catch 66.
  • spring 60 may be compressed between feed lever 52 (or a differently configured mounted member) and attachment point 56.
  • feed lever 52 or a differently configured mounted member
  • attachment point 56 may be a variety of appropriately elastic components.
  • spring 60 may be a spring with a relatively low spring rate, such that the force required to compress the spring a given distance may be relatively low.
  • spring 60 may be pre-compressed for installation on counterforce assembly 28. This may result in spring 60 applying a relatively large initial force to brake belt 54 at brake attachment point 56. Further, where the spring rate of spring 60 is relatively low, further compression of spring 60 during operation of counterforce assembly 28 may change the force applied by spring 60 at the brake attachment point 56 only by relatively small amounts. Accordingly, spring 60 may apply substantially constant force (e.g., force varying from an initial amount by 15% or less) at attachment point 56 even as the relative compression of spring 60 changes. This may be useful, for example, where a brake pad or other lining of brake belt 54 wears away during the lifespan of brake belt 54, which may require adjustments of spring 60 to maintain appropriate tension on brake belt 54.
  • Tensioning assembly 30 which may additionally (or alternatively) assist in braking or indexing pulley member 40 (and guide roller 32), may be attached to brake belt 54 (or another traction device) at brake attachment point 88.
  • Tensioning assembly 30 may also include a pivoting member that may be rotatably mounted to frame 20 at frame attachment point 90. (In certain embodiments, a non-pivoting member may alternatively (or additionally) be provided, as described in greater detail below.) In certain embodiments, and as depicted in FIG. 3 , such a pivoting member may be configured as counterknife arm 72 for baler 10.
  • support member 74 e.g., a torsion rod
  • counterknife 34 may extend between counterknife arm 72 and counterknife arm 94.
  • rotation of support member 74 e.g., via activation of actuation device 92 (e.g., a hydraulic piston) to rotate counterknife arm 94
  • actuation device 92 e.g., a hydraulic piston
  • a spring-loaded linkage may be attached to counterknife arm 72 (or a differently configured pivoting member) and to brake belt (or another traction device) at brake attachment point 88.
  • a linkage may be a lost motion linkage.
  • fixed linkage member 76 may be fixed with respect to counterknife arm 72, with a connection component (e.g., pin 124) extending into slot 130 in movable linkage member 78.
  • linkage member 78 may include brake attachment point 88.
  • Spring 84 may extend from a connection component (e.g., pin 126) of member 76 to spring-mount member 82, which may also be connected to attachment point 88.
  • Pin 124 may slide along slot 130 as linkage member 78 moves in order to guide the motion of linkage member 78. Further, when oriented by motion of linkage member 78 at an end of slot 130, pin 124 may provide a stop to prevent further movement of linkage member 78 in a particular direction.
  • a "stop" of a lost motion linkage may be an orientation of the lost motion linkage (or components thereof) at which further motion of a lost motion portion of the linkage is prevented. It will be understood that various types of stops for a lost motion linkage may be possible, including stops provided by pins and slots (as described above), stops provided by chains or cables, and stops with other configurations.
  • fixed linkage member 76 may be integrally or separately formed with its various connection components
  • spring-mount member 82 may be integrally or separately formed with moveable linkage member 78.
  • idler pulley 86 may be attached to counterknife arm 72 for controllable engagement of drive belt 42.
  • controller 96 may be provided, which may be in control communication with actuator 92 (e.g., a hydraulic piston or electric actuator), power source 46, and various other components or systems.
  • actuator 92 e.g., a hydraulic piston or electric actuator
  • controller 96 may be configured to include a computerized, electrical, electrohydraulic or other controller, which may provide an electrical, hydraulic or other signal to actuation device 92 in order to cause device 92 to rotate counterknife 94.
  • controller 96 may be configured to cause power source 46 to provide (or not provide) power to drive pulley 44.
  • controller 96 e.g., including a computerized, electronic, electrohydraulic, or other controller
  • controller 96 may be configured to activate (or deactivate) an electric motor, engage (or disengage) a clutch device, and so on, such that rotational power is provided to drive pulley 44.
  • bearing mount tensioning assembly 114 may be included to provide appropriate biasing force against guide roller 32.
  • FIGS. 4A and 4B various example components of counterforce assembly 28 are depicted in an exploded view.
  • spring 60 when spring 60 is included in assembly 28 (e.g., as secured to feed lever 52 by bracket 62), the resting compressive force on spring 60 may be adjustable.
  • spring 60 may be aligned by spring guide 106 between two spring seats 104.
  • Spring adjuster 102 e.g., a partially threaded rod
  • spring 60 may extend through spring 60 and trunnion 108, with trunnion 108 rotating with respect to bracket 62 to facilitate rotation of feed lever 52 about attachment point 58.
  • spring adjuster 102 may accordingly be utilized to change the compression of spring 60 between spring seats 104 (e.g., by rotating a threaded adjuster 102 in either direction in order to adjust the distance between spring seats 104).
  • nut 102a (or a similar feature) of spring adjuster 102 may seat on trunnion 108 to prevent extension of spring 60.
  • spring 60 may have a larger spring constant than spring 84, such that when spring 60 applies a tensioning force to brake belt 54, spring 84 may tend to elongate more than spring 60 tends to compress. Accordingly, applying tensioning force to brake belt 54 with spring 60 may cause pin 124 to be moved within slot 130 to a stop at the rightmost end (from the perspective of the figures) of slot 130. Similarly, when tensioning assembly 30 applies a tensioning force to brake belt 54 via spring 84, spring 84 may tend to elongate more than spring 60 tends to compress. This may also result in pin 124 moving to the rightmost end of slot 130 and the corresponding stop.
  • spring adjuster 102 may be utilized to pre-compress spring 60 by a particular amount prior to operation of counterforce assembly 28 (e.g., during installation of counterforce assembly 28). During operation of counterforce assembly 28, spring 60 may accordingly provide a larger initial tensioning force to brake belt 54 than if spring 60 had not been pre-compressed.
  • spring 60 may be pre-compressed (or otherwise configured) such that the initial tensioning force applied by spring 60 to brake belt 54 exceeds the maximum tensioning force that spring 84 (as configured with tensioning assembly 30) may apply to brake belt 54. Accordingly, movement of attachment point 56 by counterforce assembly 28 to increase tension on brake belt 54 may result in relatively substantial elongation of spring 84, but little or no compression of spring 60. Similarly, movement of tensioning assembly 30 to apply tensioning force to brake belt 54 may result in compression of spring 60 only after the lost motion linkage has reached a stop (e.g., after spring 84 has been elongated such that pin 124 seats against the right end of slot 130).
  • feed lever 52 may be rotatably attached to frame 20 at attachment point 58 via pivot plate 116, with plate 116 being fixed (e.g., welded) to frame 20 to provide a pivot point for the rotation of feed lever 52.
  • pulley member may be fixedly attached to guide roller 32 via guide roller extension 32a, which may extend through frame 20 and bearing mount tensioning assembly 114 (which may be welded to the frame 20).
  • Assembly 28 may be attached to brake belt 54 via loop 54a, which may be secured via a bolt or pin to mounting cap 110, on which lower spring seat 104 may be seated and through which spring adjuster 102 may pass to engage a nut or other attachment device.
  • brake belt 54 may include brake pad 112 or various other features.
  • Brake pad 112 may be configured, for example, to seat within a complimentary contour around the circumference of pulley member 40. During the limited lifespan of brake belt 54, brake pad 112 may tend to wear away. Accordingly, larger and larger displacement of attachment points 56 and 88 (from a reference position) may be required to apply the same braking force to the pulley member 40. In this regard, as also noted above, it may be useful for spring 60 to exhibit a relatively small spring rate.
  • spring 60 exhibits a relatively small spring rate
  • the length of spring 60 (and, thereby, the location of attachment point 56) may be adjusted as brake pad 112 wears, without substantially changing the tensioning force applied by spring 60 to brake belt 54.
  • spring 60 may accordingly provide a force to brake belt 54 that remains substantially constant over the lifespan of brake belt 54 (or another traction device).
  • a mounted member of assembly 28 may be configured as a rotatable feed lever (e.g., feed lever 52).
  • a catch may be provided on frame 20 to selectively prevent rotation of such a feed lever.
  • such a catch may be configured as catch 66, which may include notch 68, which may prevent counter-clockwise rotation (from the perspective of FIG. 4A ) of feed lever 52 when feed lever 52 is engaged with notch 68.
  • spring 60 may tend to press against attachment point 56 to bias feed lever 52 upward into notch 68 such that spring 60 must be actively compressed (e.g., by clockwise rotation of feed lever 52) in order to remove feed lever 52 from notch 68.
  • assembly 30 may include, in certain embodiments, a lost-motion linkage with fixed linkage member 76, movable linkage member 78 with slot 130, spring-mount member 82, spring 84, and so on.
  • spring 84 may be engaged with fixed linkage member 76 and the other end of spring 84 may be engaged with spring-mount member 82, in order to provide a spring-loaded connection between these components.
  • movable linkage member 78 may be attached to (and, in certain embodiments, include) spring-mount member 82, and may also include brake attachment point 88 (e.g., a hole through which a bolt or pin may be inserted to attach loop 54b of brake belt 54 (see FIG. also 4A)).
  • brake attachment point 88 e.g., a hole through which a bolt or pin may be inserted to attach loop 54b of brake belt 54 (see FIG. also 4A)).
  • Slot 130 (or another feature) at an opposite end of movable linkage member 78 may be slidably (or otherwise) engaged with fixed linkage member 76 in order to provide lost-motion functionality for the linkage.
  • various of these components may be formed integrally with other of the components, or may be formed as various distinct pieces.
  • spring-mount member 82 may be integrally formed with movable linkage member 78.
  • fixed linkage member 76 may include various separate components.
  • main member 76a may include lower pin 126 (or other connection component) to engage one end of spring 84, and may also include an upper opening, into which pin 124 (or other connection component) may be inserted to engage with slot 130 of movable linkage member 78.
  • Main member 76a, lower pin 126, and pin 124 may be welded together, or otherwise rigidly connected.
  • Member 76b may be configured to slide over the pins 124 and 126, in order to secure spring 84 and linkage member 78 in place. Member 76b may itself be secured in place with cotter pin arrangement 128 (see FIG. 3 ), or other mechanisms.
  • pin 124 may be fixedly attached to counterknife arm 72 (or another pivoting portion of assembly 30) in order to generally secure the linkage to counterknife 72.
  • movement e.g., rotation
  • counterknife arm 72 may generally correspond to movement of the associated linkage, with, for example, some of such movement being absorbed through lost-motion functionality provided by the components noted above.
  • slot 134 may be included in counterknife arm 72 in order to allow idler pulley 86 to be adjustably attached to counterknife arm 72 (e.g., via bolt 132). This may, for example, allow for appropriate tensioning of drive belt 42 depending on the particular orientation (i.e., degree of rotation) of counterknife arm 72. For example, with idler pulley 86 appropriately located along slot 134, idler pulley 86 may tension drive belt 42 for power transmission substantially simultaneously with release of tension from brake belt 54 (as described in greater detail below).
  • idler pulley 86 may release tension on drive belt 42 to prevent further power transmission by belt 42 substantially simultaneously with the application of braking tension to brake belt 54 (as also described in greater detail below). It will be understood that other timings for these events may also be possible, including non-simultaneous timings.
  • bushing 136 may be secured to frame 20 via bushing mount 138, with extension 140 of support member 74 extending therethrough.
  • FIGS. 6 and 7 an example operation of assemblies 28 and 30 to brake pulley member 40 (and guide roller 32) is depicted, which may assist in braking pulley member 40 (and guide roller 32).
  • power source 46 may be providing power to drive pulley 44 and, via drive belt 42, to pulley member 40 and guide roller 32 (not shown in FIGS. 6 and 7 ).
  • guide roller 32 may rotate material roll 36 (not shown in FIGS. 6 and 7 ) and guide wrap material (e.g., net wrap) between roll 36 and roller 32 toward baling chamber 18.
  • counterknife arm 72 may have been generally rotated in a clockwise direction from a reference position to the orientation of FIG. 6 , so that idler pulley 86 engages and appropriately tensions drive belt 42 for power transmission, and so that counterknife 34 has been removed from path 148 of the wrap material.
  • This clockwise rotation may have also generally moved the lost-motion linkage (e.g., members 76, 78, and 82 and spring 84) toward release pulley member 40, which may generally result in pin 124 sliding somewhat to the left (from the perspective of FIG. 6 ) within slot 130 and, correspondingly, to a release of tension from spring 84.
  • tension on brake belt 54 from tensioning assembly 30 may be released, which may reduce the braking force on pulley member 40 and thereby allow to guide roller 32 to rotate (as driven via drive belt 42).
  • clockwise rotation of counterknife arm 72 to the orientation of FIG. 6 may also correspond with controller 96 (not shown in FIG. 6 ) causing power source 46 (not shown in FIG. 6 ) to provide power to drive pulley 44.
  • controller 96 may cause the motor to activate and provide power to drive pulley 44 when counterknife arm 72 rotates to release brake force from pulley member 40 (i.e., rotates in a clockwise direction to the orientation of FIG. 6 ).
  • controller 96 may cause a clutch device to engage in order to provide power to drive pulley 44, or execute various other power-providing functionality. Such control may be effected in various known ways.
  • baler 10 appropriate movement of various components within baler 10 may activate a switch, which may provide an electrical (or other) signal to controller 96 and thereby trigger activation (or engagement) of power source 46.
  • controller 96 activates actuation device 92 (e.g., an electric actuator) to pivot counterknife arm 94 (e.g., to move counterknife 34 out of material path 148) (see FIG. 3 )
  • controller 96 may also provide an appropriate signal to power source 46 to cause power source 46 to provide rotational power to drive pulley 44.
  • tensioning assembly 30 may be rotated in a counterclockwise direction from the orientation depicted in FIG. 6 to the orientation depicted in FIG. 7 .
  • This rotation may cause the lost-motion linkage (e.g., members 76, 78, and 82 and spring 84) to move generally away from pulley member 40.
  • This may increase the force on spring 84, elongating spring 84.
  • the elongation of spring 84 may cause pin 124 to slide to the right (from the perspective of FIG. 7 ) within slot 130 until it is urged into a stop at the right end of slot 130 and thereby prevents further elongation of spring 84.
  • tension on brake belt 54 may be increased in order to provide a braking force to pulley member 40 and stop the rotation of guide roller.
  • counterforce assembly 28 may provide a resistive force to brake belt 54, in response to tensioning force from tensioning assembly 30, with little to no (further) compression of spring 60.
  • a braking operation similar to that described above may also be executed with a solid body (e.g., a solid rod) substituted for spring 60.
  • counterclockwise rotation of tensioning assembly 30 may also cause counterknife 34 (via the pivoting of counterknife arm 72) to intercept path 148 and thereby sever the wrap material (as depicted in severed path 148a).
  • a single action e.g., pivoting counterknife arm 94 with actuation device 92
  • counterclockwise rotation of counterknife arm 72 to the orientation of FIG. 7 may cause idler pulley 86 to release tension from drive belt 42 and thereby reduce (or eliminate) the ability of drive belt 42 to transfer rotational power from drive pulley 44 to pulley member 40.
  • the counterclockwise rotation of counterknife arm 72 may correspond with controller 96 causing power source 46 to cease providing power to drive pulley 44.
  • controller 96 may cause the motor to deactivate and thereby stop providing power to drive pulley 44 when counterknife arm 72 rotates to apply braking force to pulley member 40
  • controller 96 may cause a clutch device to disengage upon counterclockwise rotation of counterknife arm 72.
  • Such control may be effected in various known ways. For example, appropriate movement of various components within baler 10 may activate a switch, which may provide an electrical (or other) signal to a controller within controller 96 and thereby trigger de-activation (or disengagement) of power source 46.
  • controller 96 activates actuation device 92 (e.g., an electric actuator) to pivot counterknife arm 94 (see FIG. 3 )
  • controller 96 may also provide an appropriate signal to power source 46 to cause power source 46 to cease providing rotational power to drive pulley 44.
  • a computing device within controller 96 may count the number of rotations of the bale being wrapped or keep a timer of the wrapping operation.
  • the controller may determine that the wrapping operation is complete and may, accordingly, cause actuation device 92 to rotate counterknife arm 94 in a counterclockwise direction (see FIG. 3 ). Accordingly, and correspondingly, counterknife 34 and counterknife arm 72 may also rotate (e.g., pivot around attachment point 90), causing counterknife 34 to sever the wrap material and assemblies 28 and 30 to brake guide roller 32.
  • counterforce assembly 28 may not be rotatable with respect to frame 20 (e.g., may simply provide a spring-biased anchor at one end of brake belt 54).
  • counterforce assembly 28 may not include spring 60 or tensioning assembly 30 may not include spring 84.
  • springs 60 and 84 are both provided, however, it may be useful for spring 60 to be relatively stiffer (i.e., stronger) than spring 84. In this way, as tensioning assembly 30 is rotated into the braking orientation of FIG. 7 , spring 60 may not be excessively compressed.
  • assemblies 28 and 30 to index pulley member 40 and guide roller 32
  • a new material roll may have just been loaded into compartment 24 and wrap material from the material roll manually guided along material path 150 to the interface between guide roller 32 and roller 152. Due to the contact (or small clearance) between rollers 32 and 152, however, it may not be practical to guide the material between rollers 32 and 152 without mechanical assistance. Accordingly, the indexing functionality of assembly 30 may be employed (e.g., manually, through user engagement with handle 64) to index roller 32 and thereby feed the wrap material between rollers 32 and 152.
  • feed lever 52 may be released from catch 66 (e.g., by slightly rotating feed lever 52 in a clockwise direction to clear notch 68 (not shown in FIGS. 8 and 9 ). Where spring 60 is included, this may slightly compress spring 60.
  • feed lever 52 may be flexed (or otherwise moved) away from frame 20 in order to clear catch 66 (and, potentially, to release the slight compression of spring 60).
  • An indexing operation may then be "primed” by rotating feed lever 52 in a counterclockwise direction around attachment point 58, which may generally move attachment point 56 in a counterclockwise with respect to pulley member 40.
  • the counterclockwise rotation of feed lever 52 may release tension from brake belt 54 through the counterclockwise movement of attachment point 56. Accordingly, the tensioning force experienced by the tensioning assembly 30 at attachment point 88 may also be decreased. Where spring 84 has been previously elongated beyond its natural length, this decrease in tensioning force may result in a shortening of spring 84 toward the natural length and a corresponding movement of link 78 to the right. Accordingly, as feed lever 52 is rotated in the clockwise direction, pin 124 may be moved to the left within slot 130, away from the stop at the right end of slot 130. The shortening of spring 84 may also draw brake belt 54, via spring-mount member 82, in a counterclockwise direction around pulley member 40.
  • nut 102a may maintain spring 60 in a particular state of compression. This may usefully ensure that attachment point 58 rotates upward with feed lever 42 in order to release tension on brake belt 54. Further, this may ensure that spring 60 may apply an appropriately large initial tensioning force to brake belt 54 when feed lever 52 is pivoted in the opposite direction.
  • feed lever 52 once primed, may be pivoted around attachment point 58 in a clockwise direction.
  • spring 60 may not compress (or may compress only a small amount) as a result of this clockwise pivot of feed lever 52, with spring 60 accordingly acting as (or approximately as) a rigid member to move attachment point 56 clockwise (and downward).
  • indexing of pulley member 40 may be achieved with a rigid rod (or other member) in place of spring 60.
  • This movement of attachment point 56 may apply a tensioning force to brake belt 54 (which, in such a case may be viewed as an indexing device as well as a brake device).
  • tensioning assembly 30 may be resisted by tensioning assembly 30 at attachment point 88.
  • spring 84 may resist the tensioning force on brake belt 54 through the elongation of spring 84 from a shorter configuration (see FIG. 8 ) to an elongated configuration (see FIG. 9 ).
  • an indexing torque corresponding to the strength of spring 84 may be applied to pulley member 40 by brake belt 54, as feed lever 52 (and attachment point 56) continues its clockwise movement.
  • pulley member 40 (and guide roller 32) may be indexed in a clockwise direction to feed wrap material along extended path 150a between rolls 32 and 152.
  • pin 124 is moved to the right within slot 130, as the clockwise rotation of feed lever 52 causes a leftward movement of link 78, such that spring 84 is elongated.
  • the length of spring 60 may not substantially change during an indexing operation.
  • the strength of the indexing torque on the pulley member 40 may depend largely on the strength of spring 84 (e.g., on the spring constant of spring 84). Indeed, indexing of pulley member 40 (as described above) may still be possible even if spring 60 is replaced with a rigid rod.
  • feed lever 52 may be returned to the orientation depicted in FIG. 8 , with spring 84 returning to the shorter configuration.
  • the indexing process (e.g., the progression between the configurations of FIGS. 8 and 9 ) may then be repeated until an appropriate amount of wrap material has been fed between rolls 32 and 152.
  • Feed lever 52 may then be re-secured in catch 66 (e.g., to allow for the operation and braking of guide roller 32, as described above).
  • counterforce assembly 28 may not include spring 60 but may still function for indexing of guide roller 32 (e.g., through similar pivoting of feed lever 52 about frame attachment point 58, but with a rigid connection between feed lever 52 and brake attachment point 56).
  • certain indexing operations described above may be possible in a configuration in which tensioning assembly 28 includes no spring 84 or in which tensioning assembly 28 is not itself rotatable with respect to frame 20.
  • springs 60 and 84 are both provided, however, it may be useful for spring 60 to be relatively stiffer (i.e., stronger) than spring 84. In this way, as feed lever 52 is rotated to index guide roller 32 (e.g., moved from the orientation of FIG. 8 to the orientation of FIG. 9 ), spring 60 may not be excessively compressed and, accordingly, may not excessively absorb the potential indexing force.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Environmental Sciences (AREA)
  • Mechanical Engineering (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
  • Storage Of Harvested Produce (AREA)

Claims (8)

  1. Ramasseuse-presse (10), comprenant:
    un châssis (20);
    un système d'enveloppement de balles comprenant un rouleau de guidage d'enveloppement de surface (32);
    un ensemble de contre-couteau comprenant un élément de support (74) monté de façon rotative sur le châssis (20) et un bras de contre-couteau (72, 94) monté sur l'élément de support (74), le bras de contre-couteau (72, 94) pivotant pour amener un contre-couteau (34) à couper une enveloppe de surface lorsque l'élément de support (74) tourne par rapport au châssis (20) ;
    un élément de poulie (40) attaché au et tournant avec le rouleau de guidage (32);
    un dispositif de traction (54) qui entoure, au moins en partie, l'élément de poulie (40);
    caractérisée en ce qu'elle comprend en outre:
    un ensemble de tensionnage (30) attaché au châssis (20) à un point de fixation de châssis (90) de l'ensemble de tensionnage (30), l'ensemble de tensionnage (30) comprenant une liaison à mouvement perdu limitée par un arrêt à une plage de mouvement limitée par rapport au châssis (20), la liaison à mouvement perdu étant attachée à une première extrémité du dispositif de traction à un point de fixation de frein (88) de l'ensemble de tensionnage (30), et étant attachée à l'élément de support (74) au point de fixation de châssis (90) de l'ensemble de tensionnage (30); et
    un ensemble de contre-force (28) attaché à une second extrémité du dispositif de traction (54) à un point de fixation de frein (56) de l'ensemble de contre-force (28), et attaché de façon pivotante au châssis (20) à un point de fixation de châssis (58) de l'ensemble de contre-force (28);
    dans laquelle une rotation de l'élément de support (74) dans une direction de freinage par rapport au châssis (20) amène l'ensemble de tensionnage (30) à pivoter dans la direction de freinage afin de déplacer la liaison à mouvement perdu en direction de l'arrêt de telle sorte que l'arrêt empêche tout déplacement supplémentaire de la liaison à mouvement perdu par rapport au châssis (20), l'ensemble de tensionnage (30) appliquant de ce fait une première force de tensionnage au dispositif de traction (54), la première force de tensionnage faisant face à une résistance assurée par le premier ensemble de contre-force (28), par l'intermédiaire du point de fixation de frein (56) de l'ensemble de contre-force (28), afin d'imposer une force de freinage à l'élément de poulie (40) par l'intermédiaire du dispositif de traction (54) et de freiner de ce fait le rouleau de guidage (32); et
    dans laquelle une rotation de l'élément de support (74) dans une direction de relâchement par rapport au châssis (20) amène l'ensemble de tensionnage (30) à pivoter dans la direction de relâchement afin de déplacer la liaison à mouvement perdu à l'écart de l'arrêt, l'ensemble de tensionnage (30) réduisant de ce fait la première force de tensionnage afin de réduire la force de freinage sur le rouleau de guidage (32).
  2. Ramasseuse-presse (10) selon la revendication 1, dans laquelle l'ensemble de contre-force (28) comprend un levier d'alimentation (52) monté de façon rotative sur le châssis (20) au point de fixation de châssis (58) de l'ensemble de contre-force (28);
    dans laquelle l'ensemble de tensionnage (30) comprend un premier ressort (84) attaché à la liaison à mouvement perdu;
    dans laquelle une rotation du levier d'alimentation (52) dans une direction d'indexation autour du point de fixation de châssis (58) de l'ensemble de contre-force (28) applique une seconde force de tensionnage au dispositif de traction (54), la seconde force de tensionnage faisant face à une résistance assurée par le premier ressort (84) de l'ensemble de tensionnage (30) afin d'imposer une force d'indexation à l'élément de poulie (40) et d'indexer de ce fait le rouleau de guidage (32); et
    dans laquelle une rotation du levier d'alimentation (52) dans une direction de réinitialisation autour du point de fixation de châssis (58) de l'ensemble de contre-force (28) relâche la seconde force de tensionnage afin d'enlever la force d'indexation de l'élément de poulie (40).
  3. Ramasseuse-presse (10) selon l'une des revendications 1 ou 2, comprenant en outre:
    un loquet (66) attaché au châssis (20); et
    un second ressort (60) qui s'étend entre le levier d'alimentation (52) et le point de fixation de frein (56) de l'ensemble de contre-force (28);
    dans laquelle, avec l'ensemble de contre-force (28) dans une orientation de freinage, le second ressort (60) pousse l'ensemble de contre-force (28) dans le loquet (66), le loquet (66) empêchant de ce fait la rotation de l'ensemble de contre-force (28) dans la direction de réinitialisation afin de permettre à l'ensemble de contre-force (28) de résister à la première force de tensionnage en provenance de l'ensemble de tensionnage (30).
  4. Ramasseuse-presse (10) selon l'une des revendications 1 à 3, dans laquelle l'ensemble de tensionnage (30) comprend le bras de contre-couteau (72) attaché fixement à l'élément de support (74) au point de fixation de châssis (90) de l'ensemble de tensionnage (30) et la liaison à mouvement perdu attachée au bras de contre-couteau (72), et la liaison à mouvement perdu comprend le point de fixation de frein (88) de l'ensemble de tensionnage (30).
  5. Ramasseuse-presse (10) selon l'une des revendications 1 à 4, dans laquelle la liaison à mouvement perdu comprend en outre:
    un élément de liaison fixe (76) présentant un premier et un second composants de connexion (124, 126), l'élément de liaison fixe (76) étant attaché fixement au bras de contre-couteau (72);
    un élément de liaison mobile (78) comportant une fente (130), la fente (130) étant engagée par le premier composant de connexion (124) de l'élément de liaison fixe (76); et
    un élément de monture de ressort (82) attaché à l'élément de liaison mobile (76), le premier ressort (84) s'étendant entre l'élément de monture de ressort (82) et le second composant de connexion (126) de l'élément de liaison fixe (76);
    dans laquelle au moins un parmi l'élément de liaison mobile (78) et l'élément de monture de ressort (82) comprend le point de fixation de frein (88) attaché à la seconde extrémité du dispositif de traction (54);
    dans laquelle, lorsque l'ensemble de tensionnage (30) pivote dans la direction de freinage, le premier composant de connexion (124) est poussé dans une extrémité de la fente (130) opposée au point de fixation de frein (88), le premier composant de connexion (124) et l'extrémité de la fente (130) constituant de ce fait l'arrêt qui limite la plage de déplacement de la liaison à mouvement perdu; et
    dans laquelle, lorsque l'ensemble de tensionnage (30) pivote dans la direction de relâchement, le premier composant de connexion (124) est déplacé le long de la fente (130) en direction du point de fixation de frein (88).
  6. Ramasseuse-presse (10) selon l'une des revendications 1 à 5, comprenant en outre:
    un élément de tensionnage de courroie (86) attaché à l'ensemble de tensionnage (30); et
    une courroie d'entraînement (42) qui entoure, au moins en partie, l'élément de poulie (40);
    dans laquelle une rotation de l'élément de support (74) dans la direction de relâchement par rapport au châssis (20) amène l'ensemble de tensionnage (30) à déplacer l'élément de tensionnage de courroie (86) afin de tendre la courroie d'entraînement (42) afin d'amener la courroie d'entraînement (42) à faire tourner l'élément de poulie (40) et le rouleau de guidage (32).
  7. Ramasseuse-presse (10) selon la revendication 6, comprenant en outre:
    une poulie d'entraînement (44); et
    la courroie d'entraînement (42) qui entoure, au moins en partie, l'élément de poulie (40) et la poulie d'entraînement (44);
    dans laquelle une rotation de l'élément de support (74) dans la direction de relâchement amène automatiquement une source de puissance à fournir une force d'entraînement à la poulie d'entraînement (44) et de ce fait à l'élément de poulie (40).
  8. Ramasseuse-presse (10) selon l'une des revendications 1 à 7, comprenant en outre:
    un dispositif de commande (96) qui détermine un état de fonctionnement incluant le rouleau de guidage d'enveloppement de surface (32);
    dans laquelle, lorsque le dispositif de commande (96) détermine un premier état de fonctionnement, le dispositif de commande amène automatiquement un dispositif d'actionnement à déplacer la partie de l'ensemble de tensionnage (30) dans la direction de freinage afin d'imposer la force de freinage à l'élément de poulie (40); et
    dans laquelle, lorsque le dispositif de commande (96) détermine un second état de fonctionnement, le dispositif de commande amène automatiquement le dispositif d'actionnement à déplacer la partie de l'ensemble de tensionnage (30) dans la direction de relâchement afin de réduire la force de freinage appliquée à l'élément de poulie (40).
EP15177355.3A 2014-08-05 2015-07-17 Ramasseuse-presse Active EP2982235B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US14/452,317 US9677633B2 (en) 2014-08-05 2014-08-05 Braking and indexing assembly for rotating members

Publications (2)

Publication Number Publication Date
EP2982235A1 EP2982235A1 (fr) 2016-02-10
EP2982235B1 true EP2982235B1 (fr) 2017-08-09

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Also Published As

Publication number Publication date
BR102015018694A2 (pt) 2016-06-28
US20160037726A1 (en) 2016-02-11
US9677633B2 (en) 2017-06-13
BR102015018694B1 (pt) 2020-09-29
EP2982235A1 (fr) 2016-02-10

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